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EP1705365B1 - Injecteur de carburant avec contrôle direct de l'aiguille et amplificateur variable de course - Google Patents

Injecteur de carburant avec contrôle direct de l'aiguille et amplificateur variable de course Download PDF

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Publication number
EP1705365B1
EP1705365B1 EP06100702A EP06100702A EP1705365B1 EP 1705365 B1 EP1705365 B1 EP 1705365B1 EP 06100702 A EP06100702 A EP 06100702A EP 06100702 A EP06100702 A EP 06100702A EP 1705365 B1 EP1705365 B1 EP 1705365B1
Authority
EP
European Patent Office
Prior art keywords
piston
fuel injector
spring
injection valve
valve member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06100702A
Other languages
German (de)
English (en)
Other versions
EP1705365A2 (fr
EP1705365A3 (fr
Inventor
Rudolf Heinz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1705365A2 publication Critical patent/EP1705365A2/fr
Publication of EP1705365A3 publication Critical patent/EP1705365A3/fr
Application granted granted Critical
Publication of EP1705365B1 publication Critical patent/EP1705365B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/083—Having two or more closing springs acting on injection-valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/26—Fuel-injection apparatus with elastically deformable elements other than coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a fuel injector with direct control of the injection valve member and variable ratio according to the preamble of claim 1.
  • the document EP 1174 615 A2 refers to a fuel injector with a directly controlled injection valve member, which cooperates with a valve seat and thereby controls the fuel delivery of the injector.
  • An actuator arrangement and a hydraulic pressure booster device are provided which serve to transmit the movement of the actuator arrangement to the injection valve member.
  • the pressure booster device comprises a piston element, a sleeve as a Vorhubelement and a control chamber, wherein the actuator assembly cooperates with the piston element and exerts a retraction force on the piston element.
  • the pressure booster device is designed such that it pulls the injection valve member by the pulling movement of the sleeve from its seat under the action of an initial retraction force on the piston member.
  • the movement of the injection valve element is decoupled from the piston element, such that an initial movement of the injection valve member is transferred from its seat and a further movement of the injection valve member of the actuator assembly to the injection valve member by the fluid within the control chamber, wherein the pressure booster means a variable translation of the movement of the actuator assembly ensures the valve member.
  • a fuel injector includes a piezo actuator that actuates an injection valve member. This is acted upon via a spring element in the closing direction.
  • the fuel injector further includes a hydraulic coupling space, which includes a booster piston and the injection valve member hydraulically connects with each other.
  • a sleeve-shaped body is supported, which cooperates with an intermediate stroke stop for the injection valve member forming edge.
  • the out EP 1174 615 A2 known fuel injector has an unfavorable in terms of manufacturing technology structure due to its nested pistons.
  • the solution according to DE 10 2004 028 522.5 adheres to the disadvantage that in the realized there two-stage hydraulic translation of the stroke of a piezoelectric actuator when switching the translation creates a force jump. This means that the actuator used must generate the force jump by an additional stroke, but during this additional stroke, preferably designed as a nozzle needle injection valve member does not move. This in turn means that in this phase, no stroke control of the preferably designed as a nozzle needle injection valve member is possible. However, this represents a highly undesirable condition.
  • a fuel injector is proposed with a two-stage, hydraulic ratio of Aktorhubes that already builds in the switching phase or during the action of the first gear ratio, the force for the necessary force jump, without the injector is stationary and in particular during the switching of the first level of translation in the second stage of the translation does not come to a standstill.
  • a stroke of the injection valve member which can preferably be embodied as a nozzle needle, which can be controlled in the first transmission phase of the two-stage hydraulic transmission over a larger voltage range of the actuator.
  • This can be a part of a Pre-injection phase in the combustion chamber of an internal combustion engine to inject injected pilot set much more accurate.
  • the spring element is designed so that at the highest system pressure (Common rail pressure) after the full stroke h V the force required for the force jump is established. At lower pressures, the switching time is earlier.
  • the spring used can be displayed in various design variants. Common to all variants is the fact that the spring is as compact and small builds to have the smallest possible hydraulic volume in the control room.
  • the spring used for the bias can be formed as a plate spring, as a tube spring or as well as coil spring. Except as a separate single component, the spring can also be designed integrated on the piston element. This variant is very advantageous because it has little tolerance.
  • FIG. 1 is a longitudinal section through a proposed inventions fuel injector with direct control of the injection valve member and a variable ratio of the stroke of a piezoelectric actuator.
  • a fuel injector 1 comprises an injector body 2, which is also referred to as a holding body.
  • the injector body 2 of the fuel injector 1 is connected via a clamping nut 4 with a nozzle body 3 to a screw 5.
  • the injector body 2 comprises a high-pressure port 6, via which a cavity formed in the injector body 2 is pressurized with system pressure p CR , for example with the fuel pressure level prevailing in a high-pressure accumulator (common rail).
  • system pressure p CR system pressure
  • a nozzle chamber inlet 11 extends to a nozzle body 3 formed in the nozzle chamber 10, which surrounds an injector member 9 can be formed, for example, as a nozzle needle.
  • a pressure stage is formed on the needle-shaped injection valve member 9.
  • the needle-shaped injection valve member 9 is acted upon in the opening direction.
  • a piezoelectric actuator 8 is received in the cavity 7 of the injector 2.
  • the piezoelectric actuator 8 is shown in the illustration FIG. 1 only schematically reproduced and includes a plurality of stacked arranged piezocrystals, which undergo a change in current when current of the piezoelectric actuator 8.
  • the piezoactuator 8 expands within the cavity 7 of the injector body 2 in the vertical direction and thereby provides the forces required for actuating the injection valve member 9.
  • a Vorhubhülse 13 encloses both a first piston 12 and a second piston 14.
  • the two mutually facing end faces of the first piston 12 and the second piston 14 and the two pistons 12 and 14 surrounding Vorhubhülse 13 define a hydraulic coupling space 23.
  • the outer diameter of the Vorhubhülse 13 is denoted by d V.
  • the disc-shaped stop 18 acts on both an inner spring element 16 and an outer spring element 17, which can be formed, for example, both as spiral springs.
  • the inner spring element 16 is supported on an end face of the Vorhubhülse 13, while the outer spring element 17 is supported on a surface of the injector body 2, which in turn surrounds the Vorhubhülse 13.
  • Both the injector body 2 and the Vorhubhülse 13 lie with their the piezoelectric actuator 8 facing away from end faces along a parting line on an upper end face of the nozzle body 3.
  • the diameter of the first piston 12 is indicated by d A.
  • control chamber 20 below the second piston 14, on which the biasing spring 21 is accommodated, is the control chamber 20, in which a control chamber spring element 15 is received.
  • the control chamber spring element 15 rests on the one hand on the piston end face 19 of the second piston 14 and on the other hand is supported on an end face of the needle-shaped injection valve member 9 from. Diameter of the needle-shaped injection valve member 9 above the nozzle chamber 10 is denoted by d N.
  • FIG. 2 shows characteristic curves with respect to the switching energy, the opening pressures and the power stroke characteristic curves of fuel injectors with or without variable translator arrangement.
  • the pressure in the coupling chamber 23 is plotted over the stroke h E of the preferably needle-shaped injection valve member 9.
  • From the opening force curve 40 for a fuel injector without stepped ratio actuated piezoelectric actuator shows that its opening pressure p ⁇ , 3 is substantially below the opening pressure p ⁇ , 1 of a fuel injector, which operates with a piezoelectric actuator 8 with stepped ratio.
  • a piezoactuator 8 operating without a stepped transmission requires a switching energy indicated by the hatched area, given by the triangle abc as shown in FIG FIG. 2 ,
  • the second opening pressure p ⁇ 2 of the preferably needle-shaped injection valve member 9 of a fuel injector 1 with piezoelectric actuator 8 and step ratio is substantially lower. Therefore, a lower actuation force for the injection valve member 9 is required, so that such a piezoelectric actuator 8 has a smaller volume, ie smaller builds and therefore takes up less space.
  • a biasing spring 21 is used as proposed according to the invention, the force is continuously built up continuously from 0 until reaching the stroke h V.
  • the injection valve member 9 can therefore be driven continuously between the voltages U crit to U min , which can be a pilot injection over a larger voltage range realized, which significantly improves the precision of the pilot injection due to the fine gradation possibilities of Aktornapssbeetzschung during the first translation phase.
  • the representation according to FIG. 3 shows a variant of the biasing spring.
  • the biasing spring 21 is formed in the form of a plate spring and extends in the axial direction of the second piston 14 seen.
  • ⁇ x a lift gap is designated, which corresponds to the Vorhubweg h V.
  • S denotes the thickness of the biasing spring 21 designed as a plate spring.
  • FIG. 3 shows that the second piston 14 has a collar 22, on the support 53, the plate spring-shaped biasing spring 21 rests.
  • the biasing spring 21 is on the other hand on an end face 52 of the Vorhubhülse 13.
  • the Vorhubhülse 13 in turn is enclosed by the injector 2 of the fuel injector 1.
  • the biasing spring 21 is arranged in the lifting gap .DELTA.x.
  • Figure 3.1 shows that radial grooves 59 are formed in the end face 52 of the Vorhubhülse for pressure equalization.
  • FIG. 4 a further embodiment of a plate-shaped biasing spring is shown. From the embodiment, it is apparent that the plate spring-shaped biasing spring 21 between the collar 22, ie its support 53 and the lower end 52 of the Vorhubhülse 13 is received. The lifting gap ⁇ x.
  • the second piston 14 and the collar 22 are two separate, separate components.
  • the plate spring designed as a biasing spring 21 the biasing force is built up. The taking place due to positive engagement entrainment of the piston 14 takes place after passing through the stroke .DELTA.x. Therefore, the functions of preload and stroke are completely separated.
  • FIG. 5 shows a further embodiment of the biasing spring, designed as a tube spring.
  • the biasing spring 21 may be formed as a tube spring, which can be inserted into a receiving space 54 of the Vorhubhülse 13. According to the in FIG. 5 illustrated embodiment the biasing spring 21 is supported on an upper side 52 of the receiving space 54 on the one hand and on the support 53 of the collar 22 of the second piston 14 on the other hand. With ⁇ x the lifting gap is designated, which is identical to the Vorhubweg h V.
  • Figure 5.1 is a developed view of the lateral surface 55 of a bias spring formed as a tube spring 21 to remove.
  • the Bourdon tube has a regularly or irregularly arranged pattern of slots and circular openings which may be offset with respect to each other with respect to the axis of symmetry 51 of the biasing spring 21. Due to the design of the slit width or the diameter of the circular end portions formed, the rigidity of a bias spring formed as a tube spring 21 can be adjusted and adapted to the respective purposes in an optimal manner.
  • the representation according to FIG. 6 is to be taken as a coil spring formed biasing spring.
  • the Vorhubhülse 13 has a receiving space 54 in which the coil spring formed as a biasing spring 21 is housed.
  • the biasing spring 21 according to the in FIG. 6 illustrated embodiment is based on an upper side 52 of the receiving space 54 on the one hand and on the support 53 of the collar 22 of the second piston 14 on the other hand.
  • a designed as a spiral or coil spring biasing spring 21 is a particularly cost-effective component.
  • FIG. 7 a further embodiment of a biasing spring is shown, which is formed on a piston element.
  • an integrated spring element 56 is formed on symmetrically to the axis of symmetry 51 formed second piston 14. This may have at least one contact surface 58 which abuts against the underside of the Vorhubhülse 13. To influence the spring characteristic of the integrated spring element 56, this comprises a ring groove 57 which extends in a circular manner in the integrated spring element 56.
  • the integrally formed on the second piston 14 spring element 56 is characterized mainly by the fact that this can hardly be made tolerant. With ⁇ x the lifting gap is designated, which is identical to the stroke h V of the Vorhubhülse.
  • the representation according to FIG. 8 is a fuel injector with a directly actuated via a piezoelectric actuator injection valve member with variable translator arrangement refer.
  • FIG. 8 shows that the fuel injector 1 reproduced there analogously to the in FIG. 1 shown fuel injector has a piezoelectric actuator 8 which is disposed within a cavity 7.
  • the cavity 7 is acted upon via the high pressure port 6 with system pressure p CR from a high pressure source, not shown, with fuel.
  • the injector body 2 is connected to the nozzle body 3 via a clamping sleeve 4.
  • a piston guide 73 Located between the injector 2 and the nozzle body 3, also enclosed by the clamping sleeve 4, a piston guide 73.
  • the piston guide 73 is as well as the nozzle body 3 traversed by a nozzle chamber inlet 11, which opens into the nozzle chamber 10.
  • the piezoelectric actuator 8 acts on a first piston 12, which has an outer diameter d A.
  • the first piston 12 protrudes into the coupling space 23, in which also the collar 22, in this embodiment, is connected to the injection valve member 9.
  • the pre-lifting sleeve 13 strikes against the underside of the collar 22 and is acted upon by a spring element 70, which in turn is supported in the nozzle body 3.
  • an annular gap 71 extends in the direction of the seat of the injection valve member 9.
  • the biasing spring 21 is arranged between the underside of the piston guide 73 and the front end of the Vorhubhülse 13 facing the coupling space 23.
  • FIG. 9 From the illustration according to FIG. 9 is a plate-shaped configuration variant of the biasing spring 21 shows.
  • the biasing spring 21 is supported on the one hand next to the collar 22 lying on the end face 52 of the Vorhubhülse 13 and on the other hand on a contact surface 74 on the underside of the piston guide 73 from.
  • the Vorhubhülse 13 encloses the injection valve member 9 and is located on the underside of the collar 22 at.
  • the biasing spring 21 is effective along the stroke h V , wherein the stroke h V corresponds to the lifting gap .DELTA.x.
  • Figure 9.1 shows a developed section through the piston guide 73, at the contact surface 74 radial grooves 59 are formed for pressure equalization.
  • FIG. 10 or 10.1 are further embodiments of bias springs refer to the fuel injector according to the embodiment in FIG. 8 can be used.
  • the biasing spring 21 can be used as a Bourdon tube with an angular winding cross-section 80 as shown in FIG. 10 or as a Bourdon tube according to Figure 5.1 or also with a round spring wire cross-section as shown in FIG FIG. 10.1 be made. In both cases, the thus configured biasing spring 21 is partially embedded in the piston guide 73 and is applied to this on the contact surface 74 at. The biasing spring 21 is supported on the other hand on the end face 52 of the Vorhubhülse 13. With ⁇ x the lifting gap is designated, during which bridging a biasing force build-up takes place.
  • the inventively proposed very stiff designed biasing spring 21 can be as described above both fuel injectors according to the embodiment in FIG. 1 as well as fuel injectors according to the embodiment in FIG. 8 deploy.
  • the biasing spring 21, which can be formed both as a plate spring, as a tube spring, as a helical spring or as a spring element integrated on the piston 14, avoids the in FIG. 2 shown force jump 73 and replaces this by a continuous force buildup according to the characteristic curve 44 in accordance FIG. 2 ,
  • the force for the previously required force jump 43 can be gradually built up, without the injection valve member 9 resting, but constantly moving.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (7)

  1. Injecteur de carburant pour l'injection de carburant dans la chambre de combustion d'un moteur à combustion interne, comprenant un multiplicateur de pression à au moins deux étages ou variable, ainsi qu'un actionneur (8) avec lequel un organe de soupape d'injection (9) peut être actionné ainsi qu'un élément de précourse (13) qui, pendant le mouvement d'ouverture de l'organe de soupape d'injection (9), parcourt une distance de précourse hv jusqu'à atteindre un point de commutation du multiplicateur de pression, un élément de ressort de précontrainte (21) étant associé à l'organe de soupape d'injection (9) ou à un deuxième piston (14), et l'élément de précourse (13) étant réalisé sous forme de douille, caractérisé en ce que la douille soit entoure un premier piston (12) et un deuxième piston (14) soit est reçue de manière sollicitée par un ressort dans la région de tête de l'organe de soupape d'injection (9), et en ce que l'élément de ressort de précontrainte (21) est reçu contre une surface d'appui (53) d'un épaulement (22) du deuxième piston (14) et s'appuie sur un côté frontal (52) de l'élément de précourse (13) ou est reçu sur un côté frontal (52) de l'élément de précourse (13) et s'appuie sur une surface de butée (74) d'un guide de piston (73), de telle sorte que l'élément de ressort de précontrainte (21) augmente en continu la force requise pour faire passer le multiplicateur de pression d'une première pression d'ouverture pÖ,1 à une deuxième pression d'ouverture pÖ,2 sur une distance de précourse hv (44).
  2. Injecteur de carburant selon la revendication 1, caractérisé en ce que l'élément de ressort (56) intégré dans le deuxième piston (14) comprend une surface de contact (58) qui s'appuie sur le côté frontal (52) de l'élément de précourse (13).
  3. Injecteur de carburant selon la revendication 1, caractérisé en ce que soit sur le côté frontal (52) de l'élément de précourse (13) soit sur la surface d'appui (74) du guide de piston (73), sont réalisées des rainures radiales (59) pour la compensation de la pression.
  4. Injecteur de carburant selon la revendication 1, caractérisé en ce que l'élément de ressort de précontrainte (21) est réalisé sous forme de ressort Belleville, de ressort tubulaire, de ressort à boudin, ou sous forme d'élément de ressort (56) intégré dans le premier piston (14).
  5. Injecteur de carburant selon la revendication 4, caractérisé en ce que les enroulements de l'élément de ressort de précontrainte (21) sont réalisés sous forme rectangulaire (80), polygonale ou circulaire (81).
  6. Injecteur de carburant selon la revendication 4 ou 5, caractérisé en ce que l'élément de ressort de précontrainte (21) présente un affaiblissement de section transversale (57).
  7. Injecteur de carburant selon la revendication 1, caractérisé en ce que l'actionneur (8) est commandé pendant le passage de la distance de précourse hv (44) de manière à commander une quantité de pré-injection avec une tension comprise entre Ukrit et Umin, et en ce que l'organe de soupape d'injection (9) après le passage de l'étage du multiplicateur de pression correspondant à la distance de précourse hv (44) est déplacé en continu au-delà du point de commutation.
EP06100702A 2005-03-21 2006-01-23 Injecteur de carburant avec contrôle direct de l'aiguille et amplificateur variable de course Not-in-force EP1705365B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005012929A DE102005012929A1 (de) 2005-03-21 2005-03-21 Kraftstoffinjektor mit direkter Steuerung des Einspritzventilglieds und variabler Übersetzung

Publications (3)

Publication Number Publication Date
EP1705365A2 EP1705365A2 (fr) 2006-09-27
EP1705365A3 EP1705365A3 (fr) 2009-02-18
EP1705365B1 true EP1705365B1 (fr) 2010-11-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP06100702A Not-in-force EP1705365B1 (fr) 2005-03-21 2006-01-23 Injecteur de carburant avec contrôle direct de l'aiguille et amplificateur variable de course

Country Status (4)

Country Link
US (1) US20060208107A1 (fr)
EP (1) EP1705365B1 (fr)
AT (1) ATE487052T1 (fr)
DE (2) DE102005012929A1 (fr)

Cited By (2)

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US9038601B2 (en) 2011-11-01 2015-05-26 Cummins Inc. Flow limiter assembly for a fuel system of an internal combustion engine
US12065995B2 (en) * 2021-05-12 2024-08-20 Hitachi Astemo, Ltd Fuel injection device

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DE10326259A1 (de) * 2003-06-11 2005-01-05 Robert Bosch Gmbh Injektor für Kraftstoff-Einspritzsysteme von Brennkraftmaschinen, insbesondere von direkteinspritzenden Dieselmotoren
DE102004027824A1 (de) * 2004-06-08 2006-01-05 Robert Bosch Gmbh Kraftstoffinjektor mit variabler Aktorübersetzung
DE102006008648A1 (de) * 2006-02-24 2007-08-30 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine
JP4459183B2 (ja) * 2006-03-16 2010-04-28 株式会社デンソー インジェクタ
AT511075B1 (de) * 2011-05-26 2012-09-15 Avl List Gmbh Zweistoffbrennkraftmaschine
DE102013219225A1 (de) * 2013-09-25 2015-03-26 Continental Automotive Gmbh Piezo-Injektor zur Kraftstoff-Direkteinspritzung
CN106062350A (zh) * 2014-02-07 2016-10-26 艾克莫特公司 与压电燃料喷射器一起使用的预加载弹簧
DE102016109073B4 (de) * 2015-06-05 2022-02-17 Denso Corporation Kraftstoffeinspritzventil und Kraftstoffeinspritzventilcontroller
CN107664081A (zh) * 2016-07-29 2018-02-06 博世有限公司 用于燃料喷射器的碟形弹簧

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Publication number Priority date Publication date Assignee Title
US9038601B2 (en) 2011-11-01 2015-05-26 Cummins Inc. Flow limiter assembly for a fuel system of an internal combustion engine
US9133801B2 (en) 2011-11-01 2015-09-15 Cummins Inc. Fuel injector with injection control valve spring preload adjustment device
US9291138B2 (en) 2011-11-01 2016-03-22 Cummins Inc. Fuel injector with injection control valve assembly
US9581120B2 (en) 2011-11-01 2017-02-28 Cummins Inc. Fuel injector with injection control valve cartridge
US12065995B2 (en) * 2021-05-12 2024-08-20 Hitachi Astemo, Ltd Fuel injection device

Also Published As

Publication number Publication date
EP1705365A2 (fr) 2006-09-27
US20060208107A1 (en) 2006-09-21
DE502006008205D1 (de) 2010-12-16
EP1705365A3 (fr) 2009-02-18
DE102005012929A1 (de) 2006-09-28
ATE487052T1 (de) 2010-11-15

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